Power transmission apparatus



Sep| 7, 1937. J. W. HAMBLIN y l Pow'a 'rRANsmIssIN APPARATUS Filed Feb.v2, 1955 v 4 Sheet-s-Sh'eet 1 am; t; .Q5 1 1%. @su w 1 ,|,11 3HE u. Q H.a n .1 11 mm1 1 mw NNN @i in u ,QN

Sept. 7, 1937. J. w. HAMBLIN PWER TRANSMISSION APPARATUS 'Filed Feb. 2,1935 4 Sheets-Sheet 2 Se'pt, 7, 1937. J. w. HAMBLIN I I OWERvTRANSMISSION MPARATUS Filed Feb. 2L 1,955' l' 4 sheets-sheet s J. w.HAMBLIN POWER TRANSMISSION APPARATUS sept. 7, 1937.

4 sheets-sheet 4 ,Filed Feb. 2, 1935 Patented Sept. 7, 1937- UNITEDSTATES PATENT oFF-ICE l John W. Hamblin, Lima, Pa.

Application February Z, 1935, Serial No. 4,709

11 Claims.

'I'his invention relates to improvements in hydraulic transmissionapparatus, and more particularly to improvements in that type ofapparatus disclosed in my co-pending application for Letters PatentSerial No. 737,439, led July 28, 1934.

Among the objects in view is the improvement of the refinement ofcontrol in the precision with which power is transmitted at varyingspeeds.

A further object in view is the control of hydraulic power transmissionwith means safeguarded against unbalanced stresses whereby binding andconsequent frictional resistance to movement of parts is obviated.

Another object in view is the ready,'full, and ample supply oftransmission iluid to th'e transmission elements under all workingconditions.

A still further object inview is the simplication in construction ofparts utilized for power transmission, and a still further object is theachieving of the several advantages of the invention of my saidco-pending application in an improved manner.

With these and further objects in ViewV as will in part hereinafterbecome apparent and in part be stated, the invention includes apparatusfor hydraulicpower transmission having means for controlling variationin speed of transmission providing for exactness in such variation uatedto vary such -escape proportional to the power to be delivered.

The invention still further includes such an. arrangement of parts'wherein the controlled means of escape comprises a tapering port orexit and a valve for moving along the taper to gradually close the same.

The invention also commises such a rotor and power .deliverercoordinating with a similar rotor, and Yhydraulic-means for braking themovement of the second rotor, and means surrounding a. portion of eachof the rotors and shiftable toward the oneand toward the other forcontrolling the power transmitted by the former and thebraking action onthe latter.

The invention still further includes the lastmentioned arrangement withmeans to prevent unbalanced stress on said surrounding means.

'Ihe invention also comprises the art of power transmission includingthe step of relieving trans- 5 mission stress on hydraulic medium byreleasing a relatively thin sheet thereof, and also the further step ofvarying the width of such sheet.

The invention still further comprises certain other novel constructions,combinations, and ar- 10 rangements of parts and the art of powertransmission, all as hereinafter speciied and claimed.

In the accompanying drawings.-

Figure 1 is a longitudinal, vertical, central section through anapparatus embodying the fea- 15 tures of the present invention, partsbeing seen in elevation.

Figure 1a is a. detailed, fragmentary elevation of the abutting hubportions showing one port outlet for each hub.

Figure 2 is a transverse, vertical section approximately on the planeindicated by line 2-2 of Figure 1,'and looking in the directionindicated by the arrow, parts being seen in elevation.

Figure 3 is a similar view taken on the plane indicated by linev 3-3 ofFigure 1 and looking in the direction indicated by the arrow, partsbeing seen in elevation.

Figure 4' is also a transverse, vertical section 30 taken on the planeindicated by line 4-4 of Figure 1 and looking in the direction indicatedby the arrow.

Figure 5 is a view similar to Figure 2 taken on the plane indicated byline 5-5 of Figure 1, 35 parts being broken away forthe saving of space,and parts being seen in elevation.

Figure 6 is a view similar to Figure 2 taken on the planel indicated byline 5 6 of Figure 1 and looking in the direction indicated by the 40`arrow, parts being seen in elevation.

Figure '7 is a horizontal section taken on the plane indicated by line1-1 of Figure 5 andv looking upward, partsbeing seen 4in inverted plan.l 45 Figure 8 is a view in side elevation of the rer verse powertransmission rotor and the sleeve of the main or forward powertransmission rotor, the clutch sleeve belngomitted, parts being brokenaway for the saving of space, the 5.0 lower part'of the sleeve being'seen in longitudinal section and the vane being omitted.

' Figure 9 is a longitudinal, axial section through the clutch sleevethat is omitted from Figure 8. y

Figure 10 is a fragmentary, side elevation of 55' a part of the hubportionoi the reverse power transmission rotor as seen in Figure 8showing one of the port terminals or control exits.

In the actual operation of the apparatus dis-1 closed and claimed in myabove-identified copending application, while it is true that thetransmission of power at different speed ratios is capable of unlimitedvariation from quiescence to maximum speed, it is found that the valve'controlling' the flow of oilA or other hydraulic medium requires to bemoved to a considerable distance across the ports controlling such owbefore a suiiicient friction is set up to cause the hydraulic medium totransmit power from the rotor to its housing or to transmit brakingaction from the stationary housing to the reverse transmission rotor. Ithas been found that this is due largely to the circumferential areaallowed for free flow of the hydraulic medium, which area must bereduced to a very considerable extent .to achieve the requisite powertransmission, and. therefore, the amount of active control movement ofthe valve, that is to say movement which expresses a variation in theratio of power transmission, Ais comparatively short so that though agreat nicety of control is effected and unlimited degree in powertransmission is afforded, all of this is accomplished in such a shortextent of motion of the valve that a considerable amount of waste motionof the valve occurs in the operation of the parts of the invention of mysaid co-pending application, and the movement that is directlycontrolling must be carried out with a greater degree of precision thanwould be otherwise required if the valve movement aorded responsivenessthroughout its entire travel. The present invention overcomes thisdifficulty and provides for a valve stroke which is effectivey in powertransmission variation at substantially all places throughout thestroke.

A distinguishing characteristic between the present improved powertransmission apparatus and the structure of my above-mentioned coand maybe made up of separable 4parts rigidly.

connected and joined to avoid leakage while enpending application is thefact that inthe said copending application the parts are arranged toallow an inter-circulation between one arcuate chamber that in operationis diminishing and another arcuate chamber that in operation isincreasing in capacity, whereas in the present structure the hydraulicmedium, whether oil or other uid, is notinter-circulated directlybetween the respective arcuate chambers.

Referring to the drawings by numerals, I indicates a power shaft whichis driven from any appropriate source of power, such, for example, asthe internal combustion engine of a motor vehicle, and' 2 is the driveshaft actuated by power transmitted through an embodiment of the presentinvention from the shaft I. The 'shaft 2 may be of any of the variousforms utilized for delivering power to the differential gear of a motorvehicle, to the propeller of a ship, or to the parts to be driven of anyapparatus in which variable transmission is desirable. The shaft lextends into a housing 3 which preferably encloses all of thetransmission apparatus,

abling access to the interior by the detachment of any required sectionor part. As shown, the housing 3 consists of two main sectionsdetachably bolted together and provided with a cover 4 removably nxed tothe housing. An appropriate centering rib 5 outstands from one of thesections and facilitates location of the other `when beingssembled. Thehousing 3 is, of course, susceptible of any desired variation accordingto the details of interior construction, and is shaped to cooperate withthe contained parts, as herelnafter mentioned. The ends of the housing 3are closed except for passageway 6 at the front end to accommodate thepower shaft I, and an opening 1 at the other end to provide for thepassage of the drive shaft 2 and to accommodate a detachable cap 8closing the opening 'I and surrounding the shaft 2.

A bearing 8 is preferably set in an annular boss iii extending inwardfrom the front end of the housing 3 surrounding the opening 6, thebearing 9 consisting of the usual annular bearing housing, raceway orcone surrounded thereby and ball or roller or other anti-frictionbearings therebetween. The power shaft I extends axially lengthwise ofthe housing 3 to a point II where it substantially abuts and is axiallyalined with the inner end of the drive shaft 2. A bearing I2 similar inconstruction to the bearing 9 is seated in. an annular boss I3 whichextends inward from the 'cap 8 and surrounds and supports the shaft 2.'I'he abutting extremities of the shafts I and 2 are disposed within aboxing I4 having a front end closure I5, the boxing being made uppreferably of detachable sections secured together, as by bolts I8, orother detachable securing mea-ns, and seated within the boxing arebearings I 1 and I8, similar to bearings 9 and I2, surrounding andsupporting he respective shafts I and 2. IIhe boxing I4 is provided witha boss I9 to accommodate the bearing I8, and the said boss t9 isprovided with an axially outstanding collar 20 which is journaled torotate on a bearing 2i, similar to bearings 9, I2, I1, and I8. Bearing2| is seated in the opening 1 and abuts at one face against an annularshoulder of boss It and at the other face against the innerface of bossI3.

The boxing I4 is xed to an annular housing 22 which comprises the powerdeliverer and which surrounds and encloses the main rotor or powertransmitter 23. A centering rib 24 preferably outstands axially from thehousing 22 into an annular groove in the face of the outstanding flangedportion of the front end closure I5 to insure a snug joint between .thetwo parts, and appropriate bolts or other detachable securing means 25connect the parts to normally function as a unit while facilitatingassemblage and dismantling. Preferably formed integral with andoutstanding axiallyforwardly from the front of the housing 22 is asleeve 26 slotted longitudinally at 21, 21, the slots being arrangeddiametrically opposite each other. The forward end portion of the sleeve26 is constructed as hereinafter described to cooperate with theclutching means to at times connect with the reverse power transmissionrotor, also hereinafter described. The rotor 23 consists essentially ofa drum or cylindrical body preferably skeletonized for the saving ofWeight and having a forwardly extending hub 29 surrounding theshaft Iand preferably fixed to rotate therewith, as by a removable key 38. Thedrum making up the rotor 23, while preferably skeletonized as shown inFigures l and 2, may be otherwise formed Aso long as provided with therequisite pockets and ports; but, when skeletonized as preferred,consists of a disc comprising the rear end of the drum, a forwardlyextending flange 30, providing the periphery of the drum, and webs orpartitions 32 connecting the peripheral porf but I find three quiteeiicient.

ports 31 extend parallel to each other alongthe `pair ofvinwardly-projecting,

fingers 35 extending into guiding sockets 34, 34.'

the drum making up the rotor 23. Each pocket 3|` is proportioned toreceive and guide a radially reciprocated vane or piston 33. Each of thevanes 33 consists of a blade movable substantially radially withinv therespective pocket in va direction toward and away from shaft l, and eachhas a skirt appropriately guiding the vane when in its outer position.The said skirt may be of various forms, but preferably includesalaterally-spaced arid each resiliently stressed outward by anappropriate spring 36. Each spring 33 is preferably in the form of a.coil, and atv one end is seated against the base of the respectivesocket, and at the other end against the piston or vane 33. `As bestseen in Figure 2, each piston blade or vane 33 is provided with a recessextending from the inner end of each of the respective fingers orprojections 35 outward, and the respective spring 36 has its outer endportion extending into said recess vand seated against the' ,remainingwalll of the vane or piston blade. At one side of each piston blade orvane 33, each web or partition 32 is provided with a port 31 which islongitudinal of the respective partition and substantially radial of therotor and opening at its outer end at vthe outer face of the peripheralportion 30. The port 31 extends inward to within the hub 29 and then4extends longitudinally of the hub toward the forward end thereof, asshown in dotted lines in Figure 1, terminating just short of the forwardend of said hub. i The number of vanes 33 and ports 31 may, of course,be varied, The several hub 29 and in the same transverse planes of thehub a radially outwardly extending port or outlet opening 39communicates through the wall of the hub with each of the respectiveports 31. Each of the outlet ports or openings 39, as best seen inFigure 1a, is a slit-like opening and preferably is wedge-shaped incross section, having the larger end toward the forward end of the huband tapering rearwardly or toward the rotor 23.

Two of the outlet openings 39 are indicated in' the rotor 23 dividedinto arcuate chambers by the pistons 33. The housing making up the powerdeliverer 22 consists of an annular drum 4I and a radial web or flangeoutstanding from the sleeve 26 to and formed integral with the drum. The

, drum 4l at its rear end is provided with an outstanding flange orradial. portion 42 abutting.

against the platev I5 and connected thereto as heretofore described','I'he drum 4I is provided with an intake openingv 43v at one place of a;

tialiyhermetic seal at one place while leaving the crescent-shapedopening between the rotor and the power deliverer throughout the balance.0f the two structures, whereby, when the rotor is revolving, eachadvancing piston blade or vane 5 33 tends to crowd or compress thehydraulic agent within the arcuate chamber immediately in advance of theparticularpiston against the wall of the drum 4I to a conditionconnecting that wall with the peripheral portion 39 for 10 transmittingpower from the latter to the former; and, unless the hydraulic agent isallowed to escape through the respective port 31 communicating `with thegiven peripheral chamber, power will thus be transmitted. 0n the other15 hand, when the fluid is free to ilow through the respective port 31and through the corresponding outlets 39, the rotor 23 is permitted torotate or play freely within the power deliverer 22 without transmittingpower thereto. 20

The impeller for delivering the hydraulic agent-through the opening 43into the space between the rotor 23 and the power deliverer 22 consistspreferably of a surrounding, drum-like shell or casing 44 carried by theflange 42 en- Z5 2 circling the drum 4I, and having its end abuttingagainst the face of the ange 42, as clearly seen. in Figure 1, so thatan enclosed, annular space is provided between the shell or casing 44and the drum 4I. Impelier-like blades 45 are 30 carried bythe shell orcasing 44 and extend to the drum 4|. and are arranged in spiral relationto lthe drum, as seen in Figure 1, so that, when the power delivererrotates and the shell or casing 44 is thus rotated with its impellerblades, 35 fluid in the lower portion ofthe housing 3 will be impelledby the blade 45 against the flange 42 and along the flange to andthrough the opening 43. A portion of the space surrounded by the shellor casing 44 is preferablyclosed ofi by 40 a plate or sheet 46 extendingalong the shell or casing 44 from the trailing end of. the opening 43 toa place in advance of the leading end of said opening, so that the thusimpelled fluid will not have opportunity to escape laterally from the 45on, forward Qf and abutting against the hub ze, 5o

is a hub 41, similar to hub 29, which forms part oi' the reverse powertransmission rotor 43. The rotorl49 is seen -in axial section in Figure1, in transverse, axial section in Figure 6, and. in side elevation inFigure-8. 'I'his rotor 43 consists 55.

essentially .of a structure practically identical with that of the rotor23, but differs therefrom in being arranged in a surrounding housing 49made up largely of a part of the housing 3 and, therefore, rigid andincapable of-relative move- 60 ment. 'Ihe balance of the housing 49 nota necessary part of the housing 3 consists of an integral flange 50 atone side of the rotor 43, and an annular plate 5I at the other sidethereof detachably fixed to and within the housing 3. The rotor 48 is a.drum-like enlargement at the for- Ward end of the hub 41 and ispreferably skeletonized as described with respect to the rotor 23 with aperipheral portion forming the drum of the rotor and with fillets orpartitions 52 con- 70 necting the hub 41 with said peripheral part.'there being preferably three of such partitions,

. but, of course, a larger number may be employed the partitions 32receiving and guiding piston blades or vanes 53 urged outwardly bycoiled springs 54. Each partition 52 is also provided with a port 55opening outward into the chamber between the rotor 48 and the housing(i9, and extending inward to the hub 41 and along the hub toward therear end thereof to a point near such rear end as seen in full lines inFigure 1 and in dotted lines in Figure 8. The housing 49 is providedwith an intake opening 56 leading from a lower point in the housing 3 toenable the rotor 48 to pick up the requisite oil or other hydraulicmedium for functioning as hereinafter explained. Each prt 55 is providedalong its length in the hub 41 with a lateral outlet opening 51 seen inelevation in Figure l and in plan in Figures 1a and 19. Each outletopening 51 of each port 55 is identical with each outlet opening 39 ofeach port 31 except that each outlet opening 51 tapers in a forwarddirection while each outlet opening 39 tapers in a rearward direction.In other words, each of the outlet openings 39 and 51 tapers in thedirection toward the respective rotor.

The hub 41 is provided with a peripheral, cylindrical bearing portion 58proportioned and located to receive and serve as a bearing for theforward end portion of the sleeve 26, so that said sleeve is free torotate on the bearing 58. The forward end portion of sleeve 26 outwardof the bearing 58, that is at its outer surface, is provided with clutchteeth 59 proportioned to register with corresponding clutch teeth 60carried by the hub 41 just in rear of the rotor 48. A clutch ring 6|having an appropriate yokereceiving groove 62 is slidingly mounted onthe sleeve 26, and is provided with radially inwardlyextendinglongitudinal clutch teeth 63 registering with and `riding in the groovesbetween the clutch teeth 59, when the sleeve is in the uncoupled orunclutched position. The clutch ring 8i is proportioned to slide ontothat part of hub 41 having the teeth 69, so that the teeth 63 may enterthe grooves between the teeth 60 and afford a clutching interlockbetween the teeth 60 and 63, While portions oi the teeth 63 remaininterlocked between the teeth 59. Thus, the sleeve 26 may be clutched tothe rotor 48 or unclutched therefrom by merely sliding the ring 6I overonto the hub portion having the teeth 60, or sliding the ring back sothat it is wholly on the sleeve 26. It is preferable to have the teeth63 of different lengths at diierent places to avoid unnecessary clashingsounds when the clutch ring is moved to the clutching position. Itshould also be obvious that where silencing of the clutch action isdesired, the synchronizeremployed for that purpose as seen in myaboveidentified co-pending application may be utilized, or any otherappropriate silencer may be lemployed.

The sleeve 26, as is plainly seen in Figure 1, is of substantiallylarger internal diameter than the diameter of the hubsl 29 and 41, 'anda sleeve valve 64 is slidingly mounted on the hubs 29and 41 within thesleeve 26'.' The valve 64 consists merely of a slidingly mounted sleeveof a length equal to slightly less than the distance between the set ofport outlets 51 of hub 41 and the set of port outlets 39 of hub 29, and,in operation, it -is only necessary to shift the sleeve valve 64 across-the required port outlets 39 or 51 to control the circulation ofhydraulic medium within the respective rotor 23- or 49. To accomplishthe required sliding action. an operating ring 65 having ayoke-receiving groove 66 is mounted on the sleeve 26 and is engaged byan actuating yoke 61. The yoke 61 may, of course, be shifted in anymanner preferred otherwise than by the details 'herein disclosed, but,by preference, I utilize substantially the same structural features forshifting the ring 65 as heretofore employed in the structure shown in mycc-pending application for shifting the corresponding ring. As a matterof convenience of construction and assemblage, the ring 65 is connectedto the sleeve valve 64 by detachable pins 69, one extending through eachof the slots 21. Each of these pins consists preferably of a machinescrew threaded into the sleeve 64 and having a head seated against thesleeve valve and of a length sufficient to extend through the respectiveslot 21 and into the ring 65. The threaded or screw portion of theconnecting pin is preferably shorter than the thickness of the sleevevalve 64 so that there is no danger or likelihood of the inner end ofsuch screw portion contacting with or causing any frictionagainst'either of the hubs 29 or 41. The clutch ring 6| has its groove62 engaged by a yoke 10 preferably actuated by mechanism the same asdisclosed in my above-identified co-pending application for shifting thecorresponding clutch ring.

If the sleeve valve 64 were left subject to un- -balanced pressure,there is some likelihood that at times the valve would operate with somedifficulty from sticking or resisting longitudinal thrust. To avoid thispsibility, I provide the free endy portion of hub 29 with annulargrooves 1i, preferably one for each of the ports 31, and a communicatingpassageway 12 is provided for each port 31 to one of the respectivegrooves 1l, so that whatever pressure is developed at any time in thechambers between the pistons of rotor 23 is equalized within the sleevevalve 64, and likewise the rear end portion ,of hub 41 is provided withthree annular grooves and one of the ports 55 is formed with an opening14 for a corresponding groove 13, so that the three grooves are suppliedwith iiuid from the three ports of rotor 49, and equalization ofpressure within sleeve valve 64 with the pressure developed between thepistons of rotor I48 is thus assured.

The yoke 61 has a base 68 which is detachably carried by an actuatingplate or slide 91.v 'I'he yoke 61 maybe operated by any of numerous wellknown instrumentalities, one form of which is seen in detail in Figs. l,5, and 7, wherein the base 68 is shown as bolted or otherwiseappropriately detachably xed to a slide 91 having a toothed rack 16.meshing with the teeth ot a segmental gear 11. 'I'he gea-rv 11 is fixedto an operating shaft 18 which extends to the exterior of the housing 3and is there engaged by any appropriate operating lever or handle 19.The handle 19 may be connected to any desired control or actuator, notshown. The shifting of the valve 64 longitudinally is thus accomplishedby the movement of the lever 19 and its connected parts, whereby thevalve may be moved from a completely seated position closing the portoutlets 39 to a completely seated position closing the port outlets 51..

The parts are so proportioned that the valve may assume a neutralposition, as seen in Figure 1, where all the ports are entirely open, sothat the shaft I may be revolving, and, of course, the power transmitteror rotor 23 revolving without delivering any power in either directionto the shaft. 2. From such neutral position,4 the aoeaees valve 84 maybe moved in either direction, according to the desired direction ofrotation of the shaft 2. If the operator wishes the shaft 2 to moveinthe same direction as shaft I, which may. be considered the forwarddriving direction, it is only necessary for him to shift the lever 19 inthe direction for causing the valve 94 to move rearwardly and to c utoff more or less of the fiow through theport outlets 39. As soon as thisis done, theresistance set up by the uid that can not escape transmitspower from .the rotor 23 to the housing 22, and thence through boxing I4to the shaft 2 through the differential gears within the boxing andhereinafter to be described. Likewise, when the operator desires theshaft 2 to move in a reverse direction to the direction of rotation ofshaft I, he shifts the valve 64 from the neutral position forward toclose the port outlets 51 to a greater or less extent. In so doing, ofcourse, the port outlets 39 are left fully open, which leaves the rotor23 free to play within the housing 22 without transmitting powerthereto. Of course, before shifting the valve 64 to the position forclosing orlpartly closing the port outlets 51, the operator must seethat sleeve 29 is clutched to the rotor 48. As the valve begins to shutoff the discharge through the port outlets 51, a braking or retardingaction is caused against the rotor 48 incident to the impact of thefluid against the non-moving walls of the drum 49.

It will be readily understood bythose skilled in the art of transmissiongearing that a differential gear being arranged in the boxing I4, ashereinafter described, for transmitting motion I from shaft I to shaft2, the housing 22 will be revolving Whenever the shaft I is in motion,even though the valve 64 is :in the neutral or idling position and nopower is being transmitted from rotor 23 to the housing 22. It follows,therefore, that when the sleeve 26 and rotor 48 Aare interlocked orclutched together, and the rotor 49 is retarded in its rotation, itserves as a brake to proportionally slow down the rotation of thehousing 22 and the boxing I4 while the shaft I continues to rotate atnormal or predetermined speed, and therefore, the gearing-containedwithin the boxing I4 will transmit to the shaft 2 motion in a reversedirection and at a rate proportional to and less than the speed of shaftI `so long as the housing 22 continues to turn, de-

pending on the gear ratio of the gears in boxing I4 and the extent towhich the speed of the housing 22' has slowed down. Reverse motion may,therefore, be readily imparted to the shaft 2 by the mere shifting ofthe valve 64 to position for closing or partly closing the 'port outlets51, the speed of the reverse motion being varied and controlled by theextent to -which the discharge through-'said port outlets 51 is cut off.

The gearing in the boxing I4 may be any well known differential gear ofthe general type commonly employed in rear axle construction of motorvehicles, and may have any preferred ratio.

.For example, a gear 93 is fixed to or formed integral with the shaft Iand is preferably of the beveled and silent gear type.v Gear 93 mesheswith corresponding rightangle gears 94, 94, journaled on an appropriatespider fixed within the boxing I4, so that the gears 94 may eithertravel bodily with the gear 99 or walk thereon. Fixed to the shaft 2 orformed integral therewith within the boxing I4 is a gear 95 similar togear 93,`

and also meshing with the gears 94. Three gears 94 have been indicatedin' the accompanying drawings, and are preferred for averagelconstruction, but a greater or less number of gears 94 may be used whenand if desired. The spider for the gears 94 terminates inward in a ring96, which is of a width sufficient to enclose a double bearing 89,one'each for the terminals of the shafts I and 2. It will thus beobvious that when the shaft I is rotating and the rotor 23 istransmitting full forward driving speed, that is with the valve 84completely closing the port outlets 89, the gears 94 will be carriedwith the gear 93 and will carry with them the gear 95, so that the shaft2 is rotated in the forward direction at the same speed as the shaft I'.Now if the valve 94'be retracted somewhat, that is moved 'forwardly, anda certain amount of discharge is thereby permitted through the portoutlets 89,

there will be a proportional relative movement of the rotor 23 withrespectto the housing l22 and a corresponding lag in-the motion of thehousing 22 which will result in a proportional slowing down of therotation of the shaft 2, the gears 94 walking along the respective gears99 and 95 to compensate for this differential. The

result is not only reduction in speed, but an' increase in the force orpower with which the shaft 2 is driven relative to the power of shaft I.

Accordingly, an infinite number of variations in speed and power areavailable for transmission.

from zero to maximum from shaft I to shaft 2,1v

all accomplished by the mere shifting of the valve 94 and theproportional variation in the discharge permitted through the portoutlets 39. The tapering, slit-like form and comparatively diminutivesize of the port outlets 39 enables the cutting off.of the dischargefrom the ports 3l with a renement of precision that assures a wide rangeand smoothness of variation in the speed differential.v

For purposes of comparison, and to better aid ready appreciation of theprinciples of operation, the rotor 23 functions somewhat as a clutchwith respect to housing 22, but with available ready. slippage withoutobjectionable friction or injury, and likewise the rotor 48 functionssubstantially as a brake with respect to the xed drum 4,9 with readyslippage and without objectionable fric,-v tion or injury.

Any appropriate means may be providedfor shifting the yoke 19 for movingthe ring 6I to and. from the clutching position and thereby connectingand disconnecting the rotor 48 with revide means whereby partswhichshift the ring 95 will' operate devices for actuating the ring 6Icorrespondingly, and, to this end, a slide 91, as

best seen in Figures 5 and 7, preferably is constructed to cooperatewith and to actuate the yoke 81. Accordingly, a slide 98 is mounted inthe cover 4 in contact with-the slide 91 to at times move therewith, andto the slide 99 is fixed the yoke 19. Slideways 99, 99 and |99 aredetachably carried by the cover 4, and the slides 91 and 98 are providedwith appropriate splines or ribs slidingly mounted in grooves in saidslideways to insure accuracy and efficiency in the functioning A of thesaid slides. A lateral extension I9I (see Figure 1) projects from oneIedge of 'slide 91 into contact with the adjacent edge of slide 98 andterminates in a beveled or cammed end |92 at .one end and acorresponding beveled or cammed end |93 at the other, located, when theparts are at rest, that is en the valve 94 is in its neutral position,to havel he cam |93 contact with the rounded .projecting end, portion ofan appropriate plunger |04. reciprocally mounted within and extendingthrough the slide 98 in position to have its opposite end engage arecess |05 in the corresponding guideway 99. Likewise, the cam |02contacts with the rounded projecting end portion of a plunger |06similar in construction and arrangement to plunger |04 and adapted attimes to enter a recess |01 in the last-named guldeway 99. Each plunger|04 and |06 is stressed by an appropriate spring |09 toward the slide91. Thus, when the parts are in the position seen in Figure 7, that iswith the valve 64 in its neutral position, and the lever 19 is operatedto shift the slide 9'|.in a direction to cause the valve 84 to move overthe port outlets 39 so as to begin to slow down discharge through theports 81, the cam |03 depresses the plunger |04 into recess |05, wherebythe slide 98 is locked against possible, accidental, forward movement,and the iiat edge face of the projection IOI rides across the roundedend of the plunger |04 as the slide 91 is moving to shift the valve 64further over the port outlets 39. In fact, this relation of the slide 91with respect to the plunger |04 will continue as long as the movementsof the slide 91 are for locating the valve 94 with respect to the rotor29; but whenever the operator moves the slide 91 away from the positionof control of the port outlets 89, the cam |03 willr be moved past theplunger |04 and the plunger will thereby be allowed,l under the stressof spring |08, to move to the position seen in Figure 1, which releasesthe slide 98 and leaves it free to shift along with the guide91,-providing that the. slide is to be moved in a direction away fromthe plunger |04 and not toward it.A Thus, when the operator detiresreverse motion ln the shaft 2, and accordingly shifts slide 91 forwardlyso as to move the valve y84 into position for beginning to shut oi theiiow through the port outlets 51 of rotor 48, such movement of the slide91 will be accompanied by a corresponding movement of slide 98 incidentto the fact that the cam |02 engages the projecting rounded portionrofthe plunger |08. This movement of slide 98 with the slide 91 willcontinue until the ring 6| is in clutch with the teeth 60, and thisclutched condition is completed at or about the time when the plunger|06 reaches alinement with the depression |01, whereupon the cam |02depresses the plunger |06 into the recess |01 and thereby locks theslide 98 against further movement while the slide 91 is free to continueits forward movement and to carry with it the ring 65 and the valve 84.The straight edge portion of the projection I 0| of slide 91 rides overthe rounded end portion of plunger |08 during this further movement ofslide 91, and any desired shifting of slide 91 toward increased ordecreased reverse motion of shaft 2 may be accomplished while theplunger |08 is thus held depressed in the recess |01 and the slide 98thereby locked against movement;.

but as soon as the slide 91 is returned incident to the bringing of the`valve 64 back to neutral, the cam I 02 will in such return motion passthe lplunger |88 and allow it to spring out of recess |81, and at thesame time the cam |09 will engage the projecting end portion of theplunger |04 and thereby cause the slide 98 to move with the slide 81until the plunger |04 has reached alinement with the recess |08. Theslide 98 is substantially greater in length than the length of theslide* 81 and is of sumcIent length beyond the plunger |84 for causingthe rear end of the slide, when the plunger |84 reaches alinement withthe revalve 64 in the neutral position.

ycess |05, to abut against a detachable portion, |09

of cover 4 and prevent any further rearward sliding movement of slide98. After the reverse motion of shaft 2 is completed, and the operatordesires to drive the shaft 2 in the forward directiona return of theslide 91 is all that is required to accomplish this result. With thereturn movement, the slide 98 is restored to its normal, neutralposition as just stated, and the valve 64 may then be shifted forcausing the power transmitter or rotor 23 to impart driving force to thehousing 22.

Just above the planes of the slides 91 and 98, the cover plate 4 isformed with a tubular bore IIO which may be formed in the wall of thematerial of plate 4 or constructed as a separate part, as desired. Thelower part of the bore IIO is opened by a longitudinal slot III and apin II2 extends from within the bore I|0 through the slot III into arecess ||3 in the slide 91. Coiled springs II4, II4 are arranged in thebore IIO, one on each side of the upstanding portion of pin H2 andarranged to engage the pin, the opposite end of each spring being seatedagainst a terminal portion of the bore I I0, and the springs beingtensioned to preserve the pin I I2 at that location in the length of theslot III represented by the position of the slide 91 when the valve 64is in the neutral location. Thus, any movement of slide 91 must beagainst the pressure of one or the other of the springs II4, and thesaid springs are preferably tensioned to return the slide to the neutralposition when the parts are released, unless the operating handle 19 isheld against return movement, as by the engagement of some appropriateform of detent. A plug II5 is preferably threaded into each end portionof the bore H0 to form a seat for the respective spring I I4, so thatthe plug can be threaded along the bore as desired for increasing ordecreasing the tension of the spring lI|4 and thus insuring effectivebalance of the two springs and the proper functioning thereof to centerthe pin II2 with the To insure against over-thrust of pin II2 and itsslide 91 from any slightly unbalanced tensioning oi' springs II4 ineither direction from the centered or neutral position, the inner end ofeach spring II4 abuts against spaced fillets |29 located in the lengthof bore IIO at approximately the neutral position of the pin and betweenwhich the pin is free to move.

It should be understood that in the normal operation of the apparatus,when the shaft I is idling, that is rotating without delivering power toshaft 2, the rotor 23 will be revolving in a forward direction at fullspeedbut playing freely in the freely ycirculating huid, and at the sametime the gears 94 will be walking on the temporarily stationary gear 95incident to the action of the gear 93 on said gears 94. This walkingmovement will be at a speed according to the ratio between the gear 93and gears 94. A ratio of two to one is appropriate, though other ratiosmay be utilized when and as preferred, and if the two to one ratio isemployed, then' when the shaft I is idling, the housing 22 will berotating in the forward direction at half the speed of shaft I. 'I'heaction of the rotor 48 is simply to slow down or stop such motion of thehousing 22, and when such motion is,., completely stopped, the gear 98will directly rotate the temporary, stationarily mounted gears 94 andwill impart proportional rotation to the shaft 2, that is the shaft 2will be rotated in the reverse direction at the speed of shaft I aosaoesWhile the rotating elements or rotors above described are properlyreferred to as hydraulic, they are intended to function with anyappropriate uid .preferably possessing the least capacity forcompression, such as lubricating oil or the like.

The filling and drainage of the housing 3 may be accomplished in anypreferred manner vfrom time to time, and any well known provision forthe introduction and removal of the oil or other hydraulic medium may beprovided, such as the filler opening and drain opening customarilyprovided for motor vehicle transmission housings,

which openings are ordinarily normally retained closed by threadedplugs. Obviously, the drain out opening will be preferable at thelowermost point of the housing, and the filler opening at slightly abovethe normal liquid level to be maintained within the housing. Oneacceptable liquid level for housing 3 is substantially, on a plane justbelow the lowest point of the bearing for shafts i and 2.

As the uid is distributed throughout all the moving parts within housing3, appropriate drain f backs arepreferably 'provided wherever requiredto insure avoidance of undesirable accumulations in upper portions; and,tothat end, a port H6 leads from in advance of bearing 9, and a port H1leads from the rear of bearing I2 to lower portions ofhousing 3 fordrain back purposes. Also, it will be noted that a bearing H8 isprovided on shaft I for the forward end of rotor 48 and the rotor issupported on said bearing by an,

annular boss H9 outstanding forwardly from rotor 48 and snuglysurrounding the outerbearing ring of bearing IIB.

The action of the impeller shell or casing 44 is to 'maintain' aconstant stream of hydraulic medium discharging into or tending todischarge into the opening 43 at all times during rotation of powerdeliverer 22. Of course, at any time when one illustrative applicationof this improved art.

the power deliverer is held either retarded or inactive, the hydraulicmedium is not required for rotor 23, and at all other times thehydraulic medium is supplied in suiicient quantities for effectiveoperation. The return of such medium through the ports 31 and the portoutlets 39 provides the supply for the impeller in the course of itsrevolution. Naturally, when the port outi lets 39 are completely closed,the circulation will be discontinued and the rotor 23 will not require asupply of uid other than that locked within the arcuate chambers notincluding that chamber having the opening 43. Yet during such revolurtion, a supply will be at hand through opening 43 inventions, onerelating to the structural features that are especially efficient in thehydraulic transmission of power, and the other relating to a mode,process, or art of transmitting and controlling distribution of powerexpressed as motion, which art is susceptible of being utilized by anyof numerous, diiferent forms of apparatus. The foregoing descriptionwill serve as To insure freedom from jerks, shocks, or sudden orvotherwise objectionable changes, and to invariably provide smoothnessin the transmission of power hydraulically, and in the change of theratio of velocity of such transmission, I have found thatwhen thepressure on the hydraulic medium that serves to transit power is to bereleased or its release is to be varied for discontinuing transmissionor varying 'the speed of transmission, a stream of such medium having asubstantial bulk or body or relatively large cross section isobjectionable, and refinement and smoothness of control can better beobtained by causing the stream to be in the form of a relatively thinsheet. The sheet should bev elongated to the required degree to affordthe release and y medium to be released when the slit-like openingisfully open to completely relax the pressure on-said medium. But whenotherwise than fully open, the slit should be shaped to insure arelatively thin, wide stream flowing there-H through which can bereduced in cross section or volume escaping by shortening the width ofthe stream. Of course,` the slit need not be ina straight line, and thesheet form of the stream may be otherwise than a fiat or straight sheet,and also it is not a controlling necessity that the port outlet be theplace where the slit prois preferable to have the control means, that issome form of valve as illustrated in valve 64, so located with respectto the place where the thin sheet of outfiowing hydraulic medium occursas to control such outflow at that place.

What is claimed is:

1. In power transmission apparatus, the combination of a powerdeliverer, a power transmitter, means for compressing hydraulic mediumtherebetween, a hub outstanding from the power` transmitter and having aport leading from the compression area of the hydraulic medium, the saidport having a port outlet, a sleeve valve surrounding the hub andslidable thereon for closing and opening said port outlet, `and meansfor equalizing the pressure between the inner surface of the sleeve andthe 'compression area of the hydraulic medium.

2. The combination as claimed 1n claim 1 wherein the pressure equalizingmeans includes a circumferential `groove surrounding the hub within thesleeve with which groove the port communicates.

3. In power transmission apparatus, the combination, with a drive shaftand a power shaft for actuating the drive shaft, of a rotor connected torotate with the power shaft, a housing surrounding the rotor andconnected to deliver power to the drive shaft, the housing and rotorbeing arranged with an arcuate space therebetween, hydraulic mediumcompressing means movable between the rotor and the housing for beingreciprocated by. contact with the curved surface of a wall bounding thearcuate space, a, hub outstanding axially from the `rotor, the rotor andhub having a port leading from the area of compressed hydraulic mediumalong the hub, 'and having a port outlet through the huh-means movableacross the port outlet'for closing the same, said housingbeing formedwith an opening leading into the space between the housing and rotor,and an impeller surrounding the housing and directing and impelling thehydraulic medium through said opening into the space between the housingand the' rotor.

4. In power transmission apparatus, the combination, with a drive shaftand a power shaft for actuating the drive shaft, of a rotor connected torotate with the power shaft, a housing surrounding the rotor andconnected to deliver power to the Vdrive shaft, the housing androtorbeing arranged with an arcuate space therebetween, hydraulic mediumcompressing means movable between the rotor and the housing for beingreciprocated by contact with the curved surface of a wall bounding thearcuate space, a hub outstanding axially from kthe rotor, the rotor andhub having a port leading from the area of compressed hydraulic mediumalong the hub, and having a port outlet through the hub, means movableacross the port outlet for closing the same, and a'second rotor mountedto rotate freely and independently of the firstV rotor andI having a hubportion extending therefrom toward the hub portion of the first rotor, asec-` ond housing surrounding the second rotor; the second housing andsecond rotor being arranged with an arcuate space therebetween, a'second hydraulic medium compressing means movable between the secondrotor and the housing for arresting movement between the second rotorand the second housing, said second rotor having a passage leading fromthe the second area of compressed hydraulic medium through said hub andhaving an outlet port extending through said hub, valve means common toboth of said hubs 'and movable in one direction to control one of saidoutlet ports and movable in another direction to control the otheroutlet port, and means for coupling the second mentioned rotor with thefirst mentioned housing.

5. In power transmission apparatus, the cornbination, with a drive shaftand a power shaft for actuating the drive shaft, of a rotor connected torotate with the power shaft, a housing surrounding the rotor andconnected to deliver power to the drive shaft, the housing and rotorbeing arranged with an arcuate space therebetween, hydraulic mediumcompressing means movable between the rotor and the housing for beingreciprocated by contact with the curved surface of a wall bounding thearcuate space, a hub outstanding axially from the rotor, the rotor andhub having a port leading from the area of compressed hydraulic mediumalong the hub, and having a port outlet through the hub, means movableacross the port outlet for closing the same, and a second rotor mountedto rotate independently of therst rotor and having a hub portionextending therefrom toward the hub portions of the rst rotor, a secondhousing surrounding the second rotor, the second housing andv secondrotor being arranged with an arcuate'space therebetween, a secondlhydraulic medium compressing means movable between the second rotorandthe second housing for arresting movement of the second rotor, saidsecond rotor having a passage leading from the second area of compressedhydraulic medium through said hub and having an outlet port extendingthrough said hub, valve means common to both aoeaeee of said hubs andmovable in one direction to control one of said ou'tlet ports andmovable in another direction to control the other outlet port, and meansfor operably connecting said second rotor with the drive shaft.

6. In a power transmission apparatus, the combinatiomwith a power driveshaft and a driven shaft for receiving power therefrom, of a pluralityof rotors, one connected to rotate with the power shaft and the othernormally free to rotate independently thereof, a housing surround ingthe connected' rotor and spaced to provide a spacing for hydraulicmedium, means for exerting pressure on hydraulic medium -in said spacingfor transmitting motion from the connected rotor to its housing, asecond housing for the freely rotatable rotor and spaced therefrom toprovide a spacing for hydraulic medium, means carried by the last namedrotor for exerting pressure on the hydraulic medium for retarding andarresting relative rotation between the second housing and said lastnamed rotor, each rotor having a hub extending axially toward the otherrotor and each having a passage leading from thespace between the rotorand its housing to a point adjacent the extremity of the hub and formedwith an outlet port extending through to the exterior of said hub, valvemeans movable in one direction to control one outlet port and movable inanother direction to control the outlet port in the other hub, and meansfor connecting the freely rotatable rotor with the first-mentionedhousing.

'7. Thacombination as expressed in claim 6,

wherein the last named means includes'a reverse gear unit for drivingsaid driven shaft in a reverse direction.

8. The combination as expressed in claim 6, wherein the valve meanscomprises a sleeve surrounding said hubs and slidable thereon in onedirection to control the port in one of the hubs and in an oppositedirection to control the port in the other hub.

9. In a transmission apparatus of the class described, a drive shaft, adriven shaft, a rotor, operable by said drive shaft, an eccentrichousing surrounding said rotor having an inlet port and arranged to becoupled to said driven shaft for rotation therewith, means on said rotorfor establishing a hydraulic driving relation between the rotor andhousing when a hydraulic medium is introduced therein through said inletport, a casing surrounding said-housing and having an opening disposedin an axial direction with respect to said housing, and an impellercomprising a spiral conveying vane disposed in said opening forimpelling a hydraulic medium axially of the casing toward said port uponrotation of the housing in a hydraulic medium.

, 10. In -a transmission apparatus of the class described, a driveshaft, a driven shaft, a rotor, operable by said drive shaft, aneccentric housing surrounding said rotor having an inlet port andarranged to be coupled to said driven shaft for rotation therewith,means on said rotor for establishing a hydraulic driving relation be--tween the rotor and housing when a hydraulic medium is introducedtherein through said inlet port, a casing surrounding said housing andhaving an opening disposed in an axial direction with respect to saidhousing, an impeller comprising a spiral conveying vane disposed in saidopening for impelling a hydraulic medium axially of the casing towardsaid port upon rotarotor being formed with a discharge port leading fromthe interior of the housing to an outlet in the exterior of the rotor,and shiftable valve means for variably controlling said outlet.

11. In a transmission apparatus of the class described, a drive shaft, adriven shaft, a rotor, operable by said drive shaft, aneccentric housingsurrounding said rotor having an inlet port and arranged to be coupledto said driven shaft for rotation therewith, means on said rotor forestablishing a hydraulic driving relation between the rotor and housingwhen a hydraulic medium is introduced therein through 'said inlet port,a casing surrounding said housing and having 15 an opening disposed inan axial directionwith respect to said housing, an impeller comprisinga. spiral conveying vane disposed in said opening for impelling ahydraulic medium axially of the 'casing toward said port upon rotationof they housing in a hydraulic medium, said ro'tor being formed with adischarge port leading from the interior of the housing to an outlet inthe exterior of the rotor, shiftable valve 'means for variablycontrolling said outlet, and a housing surrounding said casing and saidimpeller for maintaining a hydraulic medium liquid level above theopening in said casing to supply the hydraulic medium to said spiralvane.

JOHN W. HAMBLIN.

